EP1840374A2 - Compressor - Google Patents

Abstract

The compressor has a working chamber (8) assigned to the opening of the fluid connection radially outside of the diameter of the drive shaft (4), where the fluid connection extends radially to the drive shaft. The compressor is arranged in the housing (1), and a propelled compressor unit is arranged over a drive shaft for sucking and compressing a refrigerant. The compressor has an oil separating device for the connection between engine area and suction gas side. The lateral working chamber opening flows into an extent recess opening to the working chamber particularly peripheral groove.

Description

The present invention relates to a compressor, in particular for motor vehicle air conditioning systems according to the preamble of patent claim 1.

Such compressors are nowadays usually produced in the form of axial piston compressors, wherein the pistons are driven by an inclination or swash plate adjustable in their inclination relative to the drive shaft, which is rotationally driven by the drive shaft. In particular, in order to prevent icing of the compressor in operation, the same is constructed so that the capacity of the compressor is controlled or regulated. This is done in such compressors in that the pressure in an engine room, which is essentially limited by a housing of the compressor, and in which, inter alia, the swash plate is controlled. By varying the engine room pressure, the inclination of the swash plate relative to the drive shaft can be varied, whereby the piston stroke and thus the delivery rate are adjusted accordingly.

To control the pressure in the engine room, however, at least one connection between a high-pressure side of the compressor and the engine room and a connection between the engine room and a suction gas side of the compressor is required. On the high pressure side, the pressure level of the compressed refrigerant is present, while on the suction gas side is a low pressure level. The connection between the low pressure side and the engine room of the compressor requires an oil separation in the area of the engine room, because the oil should lubricate the engine room and cause unnecessarily energetic losses in the plant itself. Oil, which provides for the necessary lubrication of the mechanics in the engine room (in general there is an oil mist lubrication in the engine room), thus can not reach the suction gas side.

Particularly for high-pressure compressors, for example compressors, in which CO _{2 is used} as refrigerant, a particularly efficient oil separation is necessary. For this purpose different solutions are discussed.

From the EP 0 742 116 A2 a compressor is known in which CO _{2 is used} as a refrigerant. The from the EP 0 742 116 A2 Known compressor has both a connection between the engine room and the suction gas side and between engine room and high-pressure side and works on the principle of double oil separation. In addition to a known already in compressors, which work with R134a as a refrigerant, oil separation in the high pressure chamber (where the extracted as a result of the compression process oil is separated from the refrigerant) is an additional oil separation available. The object of EP 0 742 116 A2 has for the regulation of the gas flows between the engine room and high-pressure side and engine room and suction side each a control valve for each gas stream. In addition to the already mentioned oil throw (by the compression process) on the piston of the compressor, another oil throw occurs through the gas flowing out of the engine room, since the compressor has the mentioned connection between the engine room and the suction gas side. This can hardly be prevented since, as already mentioned, an oil mist lubrication exists in the engine room, so that refrigerant led out of the engine room entrains oil in any case. Because of this problem is the subject of EP 0 742 116 A2 provided a second oil separation. For this purpose, gas emerging from the compressor, which is supplied via an external piping to the suction gas side of the compressor, is separated with regard to its oil content, the separated oil being retained by deposition in the area of the housing wall in the engine room.

In the EP 1 207 301 A2 an additional oil separator is also proposed in the mentioned connection channel. The connecting channel between the engine room and the suction side of the compressor is the subject of the EP 1 207 301 A2 integrated in a bore of the shaft and the housing. The additional oil separator is mounted on the (internal) compressor shaft end and works on the principle of centrifugal force.

Also the subject of EP 1 347 173 A2 uses the principle of centrifugal force for oil separation. The gas is sucked in through a transverse bore in the shaft. By the Centrifugal force separates the heavy drops of oil and thus less oil is sucked. A disadvantage of the principles presented z. As the sometimes high cost of additional parts and the associated costs. So will in the EP 1 347 173 A2 a lip seal proposed to avoid that not all the gas is sucked over the shaft. This solution leads to additional costs and friction losses between shaft and seal.

• es wird ein hoher konstruktiver Aufwand verursacht, da zusätzliche Teile notwendig sind und montiert werden müssen, um eine Ölabscheidung zu erreichen;
• die Verdichter gemäß dem Stand der Technik weisen, insbesondere aufgrund der Notwendigkeit zusätzlicher Teile, eine erhöhte Baugröße auf;
• die zusätzliche Ölabscheidevorrichtung verursacht zusätzliche Kosten;
• das Problem, nur einen Teil des ölbeladenen Gases dem Ölabscheider zuzuführen, indem nur ein Teil des Gases über die Welle angesaugt wird, wird entweder nicht gelöst oder durch eine Dichtung mit Mehrkosten und unerwünschten Reibeverlusten gelöst;
• die für die Fliehkraft wirksamen Radien sind relativ klein, so daß bei geringen Verdichterdrehzahlen nur ein schlechter Wirkungsgrad bzw. eine schlechte Ölabscheidung erreicht werden kann.

Disadvantages are also in all proposed principles, the small effective for centrifugal radii. This feature is to be expected with low deposition rates at low compressor speeds. The prior art compressors described above all have the following disadvantages:

• it is a high design effort caused because additional parts are necessary and must be mounted to achieve an oil separation;
• the compressors according to the prior art, in particular due to the need for additional parts, an increased size;
• the additional oil separator causes additional costs;
• the problem of supplying only a portion of the oil-laden gas to the oil separator by sucking only a portion of the gas across the shaft is either not solved or solved by a seal with additional costs and undesirable friction losses;
• the effective centrifugal force radii are relatively small, so that at low compressor speeds only poor efficiency or poor oil separation can be achieved.

Based on the above-described prior art, it is therefore an object of the present invention to provide a compressor with an oil separator for the connection between the engine room and the suction gas side, which is simple and inexpensive to manufacture and requires as little additional space caused by the Ölabscheidevorrichtung volume.

This object is achieved by a compressor with the features of claim 1, wherein advantageous developments and details of the invention are described in the dependent claims.

An essential point of the invention is therefore that there is a fluid connection between an engine compartment substantially defined by a housing of the compressor and a suction gas side, which for example is designed as a suction gas chamber may be, extends approximately radially to the drive shaft, wherein the engine compartment associated with the opening of the fluid connection is located radially outside the diameter of the drive shaft. Characterized in that the fluid connection in the radial direction not only utilizes the radius of the drive shaft itself, but a larger radius, the oil separation can be done effectively. Even at low speeds can be effectively prevented that oil reaches the suction side of the compressor. The fact that the recess is mounted in a component of the compressor, which simultaneously fulfills a further function, the number of parts can be reduced and the volume of the compressor to be minimized.

In a preferred embodiment, the opening of the fluid connection assigned to the engine compartment opens into a circumferential recess open towards the engine compartment, which may be present in particular in the form of a circumferential groove. The fluid connection may extend through a drive shaft rotatably connected to the driver for the compressor unit, which provides for the drive through. Preferably, the fluid connection comprises a recess extending in the axial direction in the drive shaft, which may be present in particular in the form of a bore. Furthermore, the fluid connection can comprise a recess extending in the radial direction through the driver and also a recess in the drive shaft which also extends in the radial direction. Both recesses are in preferred embodiments in the form of holes. The aforementioned structural features ensure a simple and cost-effective production of a compressor according to the invention.

In a preferred embodiment, a tubular outlet having a diameter smaller than the diameter of the recess in the drive shaft is disposed approximately concentric therewith and projects into it. This makes it possible that the oil which has collected on the wall of the recess or bore in the drive shaft due to the centrifugal forces with rotating shaft can not get to the suction gas side of the compressor. It should be noted at this point that a compressor can be designed very volumetric by such a construction. Such a construction with tubular outlet is conceivable both in connection with the previously mentioned features, as well as independently thereof. In particular, it should be noted at this point that such oil separation in all compressors of any type (even as the only oil separator) is conceivable. In conjunction with the features explained above comes the tubular oil barrier used as a second Ölabscheidevorrichtung or oil lock, whereby an even better oil separation is ensured.

The fluid connection can furthermore have at least one further recess extending in the radial direction in the drive shaft. This can be arranged in particular in the region of the bearing of the drive shaft, for example in a cylinder block and further in particular have the form of a bore. By this additional at least one further recess, the oil, which collects on the wall of the drive shaft, emerge from the same and at the same time lubricate the bearing of the drive shaft in the cylinder block in an arrangement of the recess / bore in the bearing.

In a further preferred embodiment, a compressor according to the invention has a cylinder block in which at least one piston is mounted reciprocably movable in a corresponding recess. The cylinder block has a conical recess arranged in the region of the tubular outlet, which is in fluid communication with the recess extending axially in the drive shaft, in particular in the region of the recess wall. As a result, the oil which adheres to the recess wall in the drive shaft, i. So z. B. the bore wall separates in the drive shaft, pass through a fluid connection in said conical recess of the cylinder block and flow from there due to the gravitational forces back into the engine room. With a corresponding arrangement, bearings, in particular the bearing of the drive shaft in the compressor, can be lubricated at the same time. On the one hand this ensures longevity of the compressor, on the other hand losses due to an increased sealing effect are reduced.

In the connection between the engine room and the suction gas side and / or between the engine room and the high-pressure side, a throttling or regulating device may be present. The throttling or regulating device may comprise an actuator and / or a control valve and / or a diaphragm. As a result, the gas flow between the engine room and the suction gas side or high-pressure side can be regulated or controlled as required.

The recess in the driver is optionally in the form of a hole with an additional (overlaid) recess. The further recess is preferably a groove extending in the direction of the bore. Alternatively or additionally, the recesses in the drive shaft, ie, the recess in the radial direction and / or the recess in the axial direction in the drive shaft in Form of holes with an additional (superimposed), be formed extending in the direction of the bore recess. Again, these are in particular additional recesses in the form of a groove. This ensures that the oil, which collects on the walls of the recess, can be selectively derived. Optionally existing further recesses in the drive shaft can of course also further recesses, for example in the form of a groove.

In a further preferred embodiment, a compressor according to the invention has an adjustable in its inclination to the drive shaft, rotationally driven by the drive shaft, in particular annular swash plate, which is in particular articulated with at least one spaced apart from the drive shaft with this co-rotating support member, wherein the support member with a co-rotating with the drive shaft power transmission element is in operative engagement. This ensures a reliable drive of a compressor according to the invention. The support element can be articulated in the radial direction and / or perpendicular thereto, in particular perpendicular to the drive shaft axis slidably on the force transmission element, thereby ensuring that the bearing between the power transmission element and the support element is configured so that on the one hand a small deformation in the storage area is ensured while at the same time the swash plate or the swivel ring can have the lowest possible height, with a consistently low Hertzian pressure is ensured in the power transmission.

In a structurally simple and thus preferred variant, the support member is formed cylinder pin. The support element may have a groove with which the force transmission element is in operative engagement. Alternatively, a pocket-shaped recess is also conceivable, wherein pocket-shaped in the sense of the present application designates in particular a rectangular or even round or elliptical recess in the support element. In this case, optionally at least the end region of the force transmission element facing the support element is in the form of a flat steel, i. So with an approximately rectangular peripheral contour formed. As a result, a secure engagement between the support element and the power transmission element is ensured with a simultaneous low design effort.

The fluid connection extends through the force transmission element in a further preferred embodiment. On the one hand a large radius compared to the drive shaft is ensured, while on the other hand, a simple and therefore cost-effective construction can be ensured. The power transmission element is optional part of the drive shaft or is optionally integrated into this or integrally formed with this. This also represents a structurally simple variant. Preferably, the support element and the force transmission element essentially serve only for the axial support of the piston or the gas power, while a device independent thereof, which may be present in particular in the form of a hinge connection between drive shaft and swash plate, the torque transmission serves. As a result, a decoupling of drive torque and gas force support is ensured, which ensures a favorable distribution of forces in a compressor according to the invention. A preferred implementation of such a hinge connection are drive bolts, which connect the swash plate to the drive shaft. Alternatively or additionally, such a compressor having a longitudinally displaceably mounted along the drive shaft sliding sleeve, on which the swash plate is pivotally mounted and which may also be connected via the drive bolt with the swash plate.

In a preferred embodiment, the fluid connection extends through the hinge connection, in particular through at least one drive bolt. This also ensures a structurally favorable connection between the engine room and the suction side.

The power transmission element may be formed at its end facing the drive shaft annular or sleeve-shaped and mounted on the drive shaft, or be in operative engagement with an annular or sleeve-shaped element which is mounted on the outer diameter of the drive shaft. Optionally, the ring-shaped or sleeve-shaped end of the force transmission element or the ring-shaped or sleeve-shaped element has at least one groove extending in the radial direction, into which at least one of the drive bolts or the device for transmitting the torque engages or engage.

The maximum and / or the minimum deflection angle of the swash plate or the swivel ring can be defined by a stop disc in a structurally simple embodiment of a compressor according to the invention. In a preferred embodiment, the fluid connection extends through at least one stop disc.

Fig. 1

eine erste bevorzugte Ausführungsform eines erfindungsgemäßen Verdichters in einer Schnittdarstellung;

Fig. 2a + b

die Antriebswelle der ersten bevorzugten Ausführungsform jeweils in Schnittansicht;

Fig. 3

eine Detailansicht der ersten bevorzugten Ausführungsform wiederum in Schnittansicht;

Fig. 4

eine Detailansicht einer zweiten bevorzugten Ausführungsform in Schnittansicht; und

Fig. 5

einen Antriebsmechanismus einer dritten bevorzugten Ausführungsform eines erfindungsgemäßen Verdichters.

The invention will now be described by way of example and with reference to the accompanying drawings in view of further advantages and features. The drawings show in:

Fig. 1

a first preferred embodiment of a compressor according to the invention in a sectional view;

Fig. 2a + b

the drive shaft of the first preferred embodiment in each case in sectional view;

Fig. 3

a detailed view of the first preferred embodiment in turn in sectional view;

Fig. 4

a detailed view of a second preferred embodiment in sectional view; and

Fig. 5

a drive mechanism of a third preferred embodiment of a compressor according to the invention.

In the explained below, preferred embodiments of a compressor according to the invention is in each case an axial piston compressor. The preferred embodiments comprise a housing 1 and a cylinder block 2. In the cylinder block 2, pistons 3 are mounted axially reciprocable. The drive of the compressor via a pulley (not shown in the figures) by means of a drive shaft 4. The pulley is driven by the engine of the motor vehicle in which the compressor is arranged.

In the preferred embodiments is a compressor with variable piston stroke, wherein the piston stroke is determined by the deflection angle of a swash plate 5. The swash plate 5 is connected via sliding blocks 6 with the piston 3 in operative engagement and is rotationally driven by the drive shaft 4 via a driver 7 which is rotatably connected to the drive shaft 4. The deflection angle of the swash plate 5 can, as known from the prior art, by a pressure change in an engine compartment 8, which is essentially limited by the housing 1 and the cylinder block 2 and in which the swash plate 5 is arranged, are influenced. The engine room 8 can with pressures between a suction pressure, so a on the inlet side of the compressor prevailing pressure, and a high pressure, ie, a prevailing at the outlet side of the compressor pressure, are acted upon.

Depending on the pressure prevailing in the engine compartment 8 or depending on the difference in the pressures on the suction side and in the engine compartment 8, a characteristic deflection angle of the swash plate 5 and thus a predetermined piston stroke and consequent pressure on the outlet side of the compressor results. The compressor power is thus regulated by means of the deflection angle of the swash plate 5 as needed, the pressure in the engine room 8 acts as a control or controlled variable. The swash plate 5 is deflected against the action of an elastic element in the form of a spring 9 from a "zero position". The drive of the swash plate 5 via the driver 7, which is in operative engagement with the swash plate 5 and as mentioned above with the drive shaft 4 is rotatably connected. The driver 7 has a recess extending in the radial direction in the form of a bore 10. This opens into a corresponding, radially extending into the drive shaft recess in the form of a further bore 11, which in turn opens into a recess in the form of a bore 12 which extends in the axial direction in the drive shaft 4. The holes 10, 11 and 12 form an integral part of the connection between the engine compartment 8 and the suction gas side of the compressor. In the first preferred embodiment (see Figures 1 and 3), the drive shaft comprises two further radially extending recesses in the form of holes 13 through which oil, which has entered the area of the bore 12 in the drive shaft 4, is deposited can be. The bores 13 are arranged in the region of the bearing (bearing 16) of the drive shaft 4 in the cylinder block 2 and ensure adequate lubrication of the bearing 16. Via a corresponding recess 14, which includes a bore 15, the gas released from the oil passes from the engine room 8 to a (not shown in the figure) throttle or control element, which is designed in the form of a control valve and controls the gas flow between the engine room 8 and the suction gas side of the compressor as needed. It should be noted at this point that instead of a control valve and throttling or other regulatory bodies come into question, such as a diaphragm or an actuator, for example in the form of a control piston. The engine-room-side opening of the fluid connection in the form of the engine-room-side end of the recess or bore 10 opens into a circumferential opening in the form of a circumferential groove 24, which is open towards the engine compartment 8.

It should be noted at this point on Fig. 3, in which an enlarged view of a section in the region of the gas outlet from the drive shaft 4 is shown. From Fig. 3 it can be seen in particular that the holes 13 in the drive shaft 4 in the region of the bearing 16 (rear radial bearing) are mounted. By the escaping residual oil, as already mentioned above, the bearings 16 are lubricated, which leads to an increased life of the compressor or to a reduced wear thereof.

As can be seen from FIGS. 2 a and b, which respectively reproduce the drive shaft 4 in a sectional view, the bore 11 has a ("superimposed") groove 17 in which the oil to be separated is collected from the gas entering via the bore 10 and along which it can drain. The groove 17 is also (not apparent from the figures) continued in the driver 7 arranged in the bore 10, so that a smooth separation of the oil or return of the same in the engine compartment 8 is possible. It should be mentioned at this point that, of course, in the region of axially extending in the drive shaft 4 recess (bore 12) one or more grooves are conceivable in which or collects the oil and then through the holes 13 in the area the bearing 16 is deposited. By varying the groove depth, it is possible, as desired, to deflect the oil flow either to the bores 13 or else to the bore 10 as required (increasing groove depth towards the corresponding recess).

In a second preferred embodiment of a compressor according to the invention, in the region of the cylinder block 2, a tubular outlet device 18 is arranged concentrically to the drive shaft 4 or to the bore 12 in the drive shaft 4. The outlet device 18 has a diameter which is smaller than the diameter of the bore 12 and protrudes into the drive shaft 4 or into the bore 12 in the drive shaft 4. The cylinder block 2 has a conical recess 19 arranged in the region of the outlet device 18. This recess is (not shown in Fig. 4) with the bore 12 in the region of its side wall 20 in fluid communication (indicated by arrows 21, which represent the flow of oil), so that the located on the side wall 20 residual oil or separated oil on the conical Recess 19 due to its weight or due to gravity in the area of the bearing 16 reach (indicated by arrows 22 and 23) and there can provide the necessary lubrication. The outlet device 18, which is formed in the present preferred second embodiment as a tube is (not shown in Fig. 4) with the suction gas side of the compressor in fluid communication or extends to the same, wherein analogous to the first preferred embodiment in the further course of the Pipe a control or throttle member is provided.

Furthermore, the compressor according to the second preferred embodiment corresponds to that according to the first preferred embodiment.

In a third preferred embodiment (see Fig. 5), the drive mechanism of the compressor according to the invention in addition to the drive shaft 4, a swash plate in the form of a swivel ring 5 'and a sliding sleeve 25 on the drive shaft 4 axially against the action of an elastic element in the form of a annular or helical fitting or return spring 26 is mounted, and a support member 27 and a power transmission element 28. The support member 27 is both radially and (in a direction perpendicular to the drive shaft axis) perpendicular to the power transmission element 28 articulated, which means that the support member 27 is slidably mounted in a plane (and not only along an axis). The support member 27 is formed cylindrically shaped and has a groove 29, by means of which the support member 27 is in operative engagement with the force transmission element 28. For this purpose, the support element 5 facing the end or is the support member 27 facing end portion of the power transmission element 28 in the form of a flat steel. This means that the said end region of the force transmission element 28 has an approximately rectangular peripheral contour. This approximately rectangular shaped end portion is engaged with the groove 29 of the support member 27. The advantage of the construction of the power transmission element 28 and the support member 27 and in particular their storage inside each other is that the flat steel does not have to build too high; the strength and rigidity (low deformation) is provided by the width of the bearing. In a central region, the strength of the force transmission element 28 increases while it is sleeve-shaped at its end facing the drive shaft 4. With the aid of the sleeve-shaped part 30 of the force transmission element 28 selbiges is mounted or fixed to the drive shaft 4. It should be noted at this point that in the present preferred embodiment, the power transmission element 28 is integrally formed and also einstoffig with the sleeve-shaped part 30. Alternatively, of course, the force transmitting element 28 and the sleeve-shaped part 30 could be two different components (possibly even of different materials). It should also be noted at this point that the force transmission element 28 or the sleeve-shaped part 30 of the force transmission element 28 has two recesses in the form of grooves 31.

Since the inner diameter of the spring 26 is greater than the outer diameter of the sleeve-shaped part 30 of the force transmission element 28, the sleeve-shaped part 30 can be pushed under the spring 26 in the assembled state of the swashplate mechanism become. This means that the sleeve-shaped part 30 is placed over the drive shaft 4 and radially fixed by the spring 26 on the drive shaft 4. On the side facing away from the spring 26 of the power transmission element 28, the sliding sleeve 25, which has a recess 32 corresponding to the force transmission element 28, is then slipped over the drive shaft 4. The sliding sleeve 25 also has two recesses in the form of holes 33. Axially the force transmission element 28 and the sliding sleeve 25 are secured by a nut on the drive shaft 4. For a better starting behavior of the compressor, a plate spring is further arranged on the drive shaft 4, which ensures that the compressor does not start at a minimum deflection angle of the pivot ring 5. Further, 4 stops in the form of stop plates 34, 35 are arranged on the drive shaft, which limit the deflection angle of the pivot ring. The stop disc 34 serves as a stop for a minimum deflection angle, while the stop plate 35 serves as a stop for a maximum deflection angle of the pivot ring 5.

The support member 27 is mounted in a cylindrical recess in the form of a bore 36 in the pivot ring 5 '. The bore 36 extends perpendicular to the drive shaft axis. The backup of the support member 27 in the pivot ring 5 'by means of two snap rings 37th

It should be noted at this point that the power transmission element 28, which in the present preferred embodiment is non-rotatably connected to the drive shaft 4, in other embodiments also rotatably with the same can be in operative engagement. It should also be noted at this point that the drive shaft 4 is not broken through the sleeve-shaped formation or the sleeve-shaped part 30 of the force transmission element 28 and thus has corresponding stability. The clear width of the bore of the pivot ring 5 'is at least slightly larger than the corresponding extent of the force transmission element 28th

In the present preferred embodiment, the mechanism of support member 27 and power transmission member 28 is not intended to transmit the torque from the drive shaft 4 to the pivot ring 5 '. The bearings between the support member 27 and power transmission element 28, between the power transmission element 28 and drive shaft 4 and between the support member 27 and pivot ring 5 'are not designed to transmit torque. It therefore eliminates a kind of driving function for the support member 27 and the power transmission element 28. This is deliberately chosen for reasons of hysteresis, ie the tilting of the pivot ring 5 'and The torque transmission is functionally decoupled from each other. The mechanism of power transmission element 28 and support member 27 essentially receives the piston forces. The torque in turn is transmitted from the drive shaft 4 to the swivel ring 5 'by a tilting joint (realized by drive bolt 38) provided on the drive shaft centerline. The torque between the sliding sleeve 25 and the pivot ring 5 'transmitting drive bolts 38 are locked or secured to the pivot ring with snap rings 39. The swivel ring 5 'has flats 40 which correspond to flats 41 on the sliding sleeve 25. In principle, it is also conceivable in other embodiments for the sliding sleeve 25 to be omitted and for the torque transmission to take place in any desired form between the drive shaft and the swivel ring 5 'directly (eg via flats on the drive shaft 1 and the swivel ring 5').

By decoupling the torque transmission and the gas power support can be achieved that in addition to the ability to dimension the support member 27 and the power transmission element 28 correspondingly small, an optimized surface pressure, in particular between the power transmission element 28 and support member 27 and between support member 27 and pivot ring 5 'can be achieved , As a result, and by the invention-specific design of support member 27 and power transmission element 28 and by the invention-specific articulation between the power transmission element 28 and support member 27, a compact design of the compressor can be achieved.

For the fluid connection between the engine compartment 8 and the exhaust gas side, in the third preferred embodiment, three different variants are conceivable for the engine room side opening into which the fluid can enter. In a first variant, an approximately radially extending bore 42 in the force transmission element 28 is arranged. This is in fluid communication with a corresponding bore 43, which likewise extends radially into the drive shaft 4, so that through the bores 42, 43 the gas can enter into the bore extending in the axial direction in the drive shaft.

In a second variant, bores 44 extending approximately in the radial direction are arranged in the drive bolt 38. These are in fluid communication with two corresponding bores in the drive shaft 4 (not shown in FIG. 5), so that in this variant, the gas from the engine compartment 8 in the extending in the axial direction bore in the drive shaft 4 can occur.

In a third variant, a bore 45 extending approximately in the radial direction is arranged in the stop disk 35, which in turn is in fluid connection with the axial bore in the drive shaft 4.

It should be noted at this point that in the third preferred embodiment, of course, further in the axial direction extending recesses or holes in the drive shaft 4 and in other components are conceivable, so as a lubrication of bearings analogous to the first two preferred embodiments ensure (not shown in Fig. 5). It should also be noted that it is not necessarily round holes in the holes 42, 43, 44, 45, but that in particular an embodiment with a "superimposed groove" according to the above-described first two embodiments is conceivable and advantageous.

Finally, it should again be pointed out that in a compressor according to the invention due to the radially extending recesses having a large radius (indicated by R in Fig. 1) with respect to the shaft center, a comparison with the prior art significantly improved oil separation is made possible , The long channel or recess with the large radius R is effective even at low speeds, so that only small oil droplets can enter the axial bore of the drive shaft 4, which are then deposited on the wall thereof. For the entire speed spectrum (especially for low speeds) of the compressor thus a good oil separation is guaranteed. Since an oil separation is already made during or before the entry of the gas into the drive shaft 4, this can also be regarded as quasi an oil entry barrier.

A suitable geometry, in particular the bores 10, 12 and 42, 43, 44, 45, which have a groove 17, allows the oil to be separated can collect in the same and then passes back into the engine compartment 8. The additional recesses or holes 13 in the drive shaft 4, which are mounted in the region of the bearings 16, ensure good lubrication of the same. In the second preferred embodiment, this is achieved by a conical recess 19, which ensures that the excreted residual oil can run in the area of the bearings 16. Both embodiments thereby realize a second Ölabscheidevorrichtung, which has the following advantages: The lubricated bearings 16 between cylinder block 2 and drive shaft 4 are additionally sealed, so that a sealing function can be taken to the outside and an additional sealing element is not necessary. The oil separation efficiency is further improved.

Although the invention will be described with reference to various embodiments with a fixed combination of features, it also includes the conceivable further advantageous combinations of these features, as they are given in particular, but not exhaustive, by the subclaims. All disclosed in the application documents features are claimed as essential to the invention, as far as they are new individually or in combination over the prior art.

LIST OF REFERENCE NUMBERS

1

casing

2

cylinder block

3

piston

4

drive shaft

5

swash plate

5 '

swivel

6

slide

7

takeaway

8th

Machine Room

9

feather

10, 11, 12, 13

drilling

14

recess

15

drilling

16

camp

17

Groove.

18

outlet

19

recess

20

Side wall

21,22,23

arrow

24

circumferential groove

25

sliding sleeve

26

Fitting or return spring

27

support element

28

Power transmission element

29

groove

30

sleeve-shaped end of the force transmission element 28th

31

groove

32

recess

33

drilling

34, 35

stop disc

36

drilling

37

snap ring

38

drive pin

39

snap ring

40

Flattening on the pivot ring 5 '

41

Flattening on the sliding sleeve 25th

42, 43, 44, 45

drilling

Claims (26)

Compressor, in particular axial piston compressor, further in particular for use in the air conditioning system of a motor vehicle, with a housing (1) and in the housing (1) arranged, via a drive shaft (4) driven compressor unit for sucking and compressing a refrigerant which a fluid connection between an engine compartment (8) defined essentially by the housing (1) and a suction gas side, in particular a suction gas chamber,
characterized in that
the fluid connection extends approximately radially to the drive shaft (4), wherein the engine compartment (8) associated with the opening of the fluid connection is located radially outside the diameter of the drive shaft (4). Compressor according to claim 1,
characterized in that
the engine-room-side opening opens into a circumferential recess, in particular a circumferential groove (24), which is open toward the engine compartment (8). Compressor according to claim 1 or claim 2,
characterized in that
the fluid connection extends through a driver (7) for the compressor unit that is connected in a rotationally fixed manner to the drive shaft (4). Compressor according to one of the preceding claims,
characterized in that
the fluid connection comprises a recess extending in the axial direction, in particular bore (12) in the drive shaft (4). Compressor according to one of the preceding claims,
characterized in that
the fluid connection comprises a recess extending in the radial direction through the driver (7), in particular a bore (10) and a recess extending in the radial direction, in particular a bore (11) in the drive shaft (4). Compressor according to claim 4 or 5,
characterized in that
a tubular outlet means (18) having a diameter which is smaller than the diameter of the recess (12) in the drive shaft (4), is arranged approximately concentrically with the drive shaft (4) and projects into the recess (12). Compressor according to one of the preceding claims,
characterized in that
the fluid connection comprises at least one further recess extending in the radial direction in the drive shaft (4), in particular bore (13), which is arranged in particular in the region of a bearing (16) of the drive shaft (4). Compressor according to one of claims 6 or 7 with a cylinder block (2), in which at least one piston (3) is mounted back and forth,
characterized in that
the cylinder block (2) has a conical recess (19) which is arranged in the region of the tubular outlet device (18) and which is connected to the recess (12) extending axially in the drive shaft (4), in particular in the region of the side wall (20) of the recess (20). 12) is in fluid communication. Compressor according to one of the preceding claims,
characterized in that
in the fluid connection between the engine room and the suction gas side a throttle or regulating device is arranged. Compressor according to claim 9,
characterized in that
the throttling or regulating device comprises an actuator and / or a control valve and / or a diaphragm. Compressor according to one of claims 5 to 10,
characterized in that
the recess in the driver (7) is a bore (10) with an additional, extending in the direction of the bore recess, in particular in the form of a groove (17). Compressor according to one of claims 4 to 11,
characterized in that
the recess in the drive shaft (4) in the radial direction and / or the recess in the drive shaft (4) in the axial direction, a bore with an additional extending in the direction of the bore recess, in particular in the form of a groove (17). Compressor according to one of the preceding claims,
characterized in that
the compressor unit has an inclination to a drive shaft (4) adjustable, of the drive shaft (4) rotationally driven, in particular annular swash plate (2) comprising at least one at a distance from the drive shaft (4) with this co-rotating support member (27) - In particular articulated - is connected, wherein the support element (27) with a co-rotating with the drive shaft (4) power transmission element (28) is in operative engagement. Compressor according to claim 13,
characterized in that
the support element (27) in the radial direction and / or perpendicular thereto, in particular perpendicular to the drive shaft axis, is articulated on the power transmission element (28). Compressor according to claim 13 or 14,
characterized in that
the support element (27) is designed as a cylinder bolt. Compressor according to one of claims 13 to 15,
characterized in that
the support element (27) has a groove (29) with which the force transmission element (28) is in operative engagement. Compressor according to one of claims 13 to 16, in particular claim 16,
characterized in that
at least of the support element (27) facing the end region of the force transmission element (28) in the form of a flat steel, ie, formed with an approximately rectangular peripheral contour. Compressor according to one of claims 13 to 17,
characterized in that
the fluid connection extends through the force transmitting member (28). Compressor according to one of claims 13 to 18,
characterized in that
the power transmission element (28) is part of the drive shaft (4) or integrated in this, in particular integrally formed therewith. Compressor according to one of claims 13 to 19,
characterized in that
the support element (27) and the force transmission element (28) serve essentially only for the axial support of the piston or gas force support, while a device independent of this, in particular a hinge connection (38), between drive shaft (4) and swash plate (5, 5 ') essentially only the torque transmission is used. Compressor according to one of claims 13 to 20,
characterized in that
the swashplate (5, 5 ') is pivotably mounted on a sliding sleeve (25) mounted axially displaceably along the drive shaft (4), and in that the swashplate (5, 5') is connected to the sliding sleeve (25) via drive bolts (38) and / or the drive shaft (4) is connected. Compressor according to claim 20 or 21,
characterized in that
the fluid connection extends through the hinge connection, in particular through at least one drive bolt (38). Compressor according to one of claims 13 to 22,
characterized in that
the force transmission element (28) at its the drive shaft (4) facing the end ring-shaped or sleeve-shaped and is mounted on the drive shaft (4) or with an annular or sleeve-shaped element is in operative engagement, which is mounted on the outer diameter of the drive shaft (4) , Compressor according to claim 23,
characterized in that
the ring-shaped or sleeve-shaped end (30) of the force transmission element (28) or the ring-shaped or sleeve-shaped element has at least one groove (31) extending in the axial direction, into which at least one or the drive bolt (s) (38) or the device (s) for transmitting the torque engages or intervene. Compressor according to one of claims 13 to 24,
characterized in that
the maximum and / or the minimum deflection angle of the swashplate (5, 5 ') is defined by a stop disc (34, 35). Compressor according to claim 25,
characterized in that
the fluid connection extends through at least one stop disc (34, 35).

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